CN108463676A - Refrigerating circulatory device - Google Patents
Refrigerating circulatory device Download PDFInfo
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- CN108463676A CN108463676A CN201780006360.4A CN201780006360A CN108463676A CN 108463676 A CN108463676 A CN 108463676A CN 201780006360 A CN201780006360 A CN 201780006360A CN 108463676 A CN108463676 A CN 108463676A
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- refrigerant
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- liquid
- phase
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/16—Receivers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
Abstract
The air conditioner (1) of the present invention has：1st relief portion (51) makes the pressure of the mixed non-azeotropic refrigerant flowed out from condenser (4) reduce to the state of gas-liquid two-phase；The mixed non-azeotropic refrigerant for the state for being decompressed to gas-liquid two-phase is separated into gas phase and liquid phase by gas-liquid separator (11)；1st path (121), the refrigerant of the gas phase into evaporator (6) supply gas-liquid separator (11)；2nd path (122) makes the refrigerant detour evaporator (6) of the liquid phase in gas-liquid separator (11)；Intercooler (13) makes its condensation by making to carry out heat exchange between the refrigerant flowed in the 1st path (121) and the refrigerant flowed in the 2nd path (122)；2nd relief portion (52) makes the pressure of the refrigerant flowed in the 1st path (121) reduce；And the 3rd relief portion (53), so that the pressure of the refrigerant flowed in the 2nd path (122) is reduced.
Description
Technical field
The present invention relates to a kind of refrigerant circuits for having and being sealed with mixed non-azeotropic refrigerant, can be used as to carry out
The air conditioner of heating operation or the refrigerating circulatory device of water heater.
Background technology
Currently, air conditioner or water heater etc. are used using in the device of refrigeration cycle using R410A as the HFC of representative
(hydrofluorocarbon (hydrofluorocarbon)) refrigerant, but in the case where greenhouse effects of the earth in order to prevent strengthens the background of limitation, just
In the exploitation for promoting GWP (Global-warming potential (global warming potential)) low refrigerant.It is less than as GWP
The candidate of the refrigerant of R410A (GWP=2090) has R32 (GWP=675), R1234yf (GWP=4) and R1234ze (E)
(GWP=6), there is CO in natural series coolant2(GWP=1) etc..
Wherein, R32 is as the functional of refrigerant, but GWP ratio R1234yf and R1234ze (E) are high.From now on, it is desirable that
The further reduction of GWP.
With R32 on the contrary, the GWP of R1234yf and R1234ze (E) are good, but performance ratio R32 and R410A is poor.
From the viewpoint of required GWP and performance, flammability etc., the exploitation of various refrigerants is advanced, but be difficult
Meet these requirements by single refrigerant.Refrigerant of more than two kinds is mixed with regulated proportion to use it is therefore proposed that having
(for example, patent document 1).
In the air conditioner of patent document 1, with the 1st refrigerant be 80wt%, the 2nd refrigerant for 20wt% mixing ratio
The R32 and R134a (or R1234yf) as the 2nd refrigerant used as the 1st refrigerant.
Here, when being used in mixed way the non-azeotropic refrigerant of different boiling as R32 and R134a (or R1234yf), exist
Temperature glide (Temperature glide, temperature gradient).
For condensation, temperature glide is the temperature difference that the temperature that condensation starts terminates with condensation.Condense start temperature
Different according to refrigerant from condensation end temp, the high R134a of boiling point first liquefies, and the R32 of low boiling point liquefies later, therefore
Generate temperature glide.About temperature glide, in the case of 2 kinds of mix refrigerants, for example, 6 DEG C or so, 3 kinds of mix refrigerants
In the case of, such as also can reach 13 DEG C or so.It is difficult to consider this temperature glide to set up the range of operation of refrigeration cycle.
In patent document 1, the concentration height (80wt%) in the R32 of refrigerant circuit is enclosed, therefore temperature glide is small.And
And the position of the defined volumetric ratio of the heat exchanger functioned as condenser in refrigerating operaton connects gas-liquid separation
Device makes the saturated vapor refrigerant rich in R134a detached from the liquid refrigerant rich in R1234yf return to condenser, via
The mechanism of decompressor is guided to evaporator, thus inhibits temperature glide.
Conventional art document
Patent document
Patent document 1：Japanese Patent Publication 2012-236884 bulletins
Invention content
The invention technical task to be solved
The boiling point of R1234yf low GWP and R1234ze (E) and R32 differ widely, if therefore improve R1234yf and
The mixed proportion of R1234ze (E), then temperature glide become larger.
If temperature glide is big, when the operation of heating uses such as heating, in the outdoor heat functioned as evaporator
Exchanger generates frosting.The temperature of the refrigerant flowed in evaporator will not become external air temperature or more, therefore for example
External air temperature is 7 DEG C and temperature glide is 10 DEG C, then it is temperature condition below freezing to become evaporation start temperature, can not
Generate the frosting to evaporator with avoiding.Therefore, in the refrigerating circulatory device of heating use, it is difficult to reduce GWP.
As shown in fig. 7, the size of temperature glide changes according to the concentration of the R32 in condensation and evaporation respectively.Fig. 7
Shown in example, in the either case for condensing and evaporating, when R32 concentration is about 20wt%, temperature glide is maximum, and with
The concentration for R32 is got higher, and temperature glide becomes smaller.
In patent document 1, on the basis of the midway of condenser makes refrigerant branch and carries out gas-liquid separation, gas phase is made to return
Condenser is returned, but the inhibition of thus obtained temperature glide is limited, in contrast to this, is enclosed in refrigerant circuit
When the concentration of R32 is high, it is more conducive to the inhibition of temperature glide.In patent document 1, the ratio of R134a or R1234yf rest on 10
~20%, therefore fail fully to reduce GWP.
By the above, the system that GWP is small in mixed non-azeotropic refrigerant can be improved the object of the present invention is to provide a kind of
The mixed proportion of cryogen, and avoid generating frosting, temperature glide is inhibited into the system in the degree that can be suitable for heating use
SAPMAC method device.
Means for solving technical task
The present invention is a kind of refrigerating circulatory device, is sealed with mixed non-azeotropic refrigerant, has and includes compressor, the 1st
Heat exchanger, relief portion and the 2nd heat exchanger and the refrigerant circuit constituted, and the heating of heat load can be carried out, the system
SAPMAC method device is characterized in that having：1st relief portion makes any from as the 1st heat exchanger and the 2nd heat exchanger
The pressure of the mixed non-azeotropic refrigerant of a condenser outflow is reduced to the state of gas-liquid two-phase；Gas-liquid separator will depressurize
Mixed non-azeotropic refrigerant to the state of gas-liquid two-phase is separated into gas phase and liquid phase；1st path, to as the 1st heat exchanger
And the refrigerant of the gas phase in the 2nd another the evaporator supply gas-liquid separator in heat exchanger；2nd path, not to steaming
Hair device supplies the refrigerant of the liquid phase in gas-liquid separator but makes its detour；Intercooler is flowed by making in the 1st path
Heat exchange is carried out between dynamic refrigerant and the refrigerant flowed in the 2nd path to make its condensation；2nd relief portion, makes the 1st
The pressure of the refrigerant flowed in path is reduced；And the 3rd relief portion, so that the pressure of the refrigerant flowed in the 2nd path is reduced.
In the refrigerating circulatory device of the present invention, preferably have in the 2nd path：Accumulator receives liquid phase from gas-liquid separator；
And valve, the flow path that can be opened and closed between gas-liquid separator and accumulator or the flow for adjusting the refrigerant flowed in flow path.
In the refrigerating circulatory device of the present invention, preferably mixed non-azeotropic refrigerant includes the R32 and work as the 1st refrigerant
For at least one of the R1234yf and R1234ze (E) of the 2nd refrigerant, all non-azeotrope mixing in refrigerant circuit is enclosed
A concentration of 30~70wt% (30wt% or more, 70wt% or less) of the 1st refrigerant in refrigerant.
In the refrigerating circulatory device of the present invention, preferably mixed non-azeotropic refrigerant includes the CO as the 3rd refrigerant2, envelope
Enter a concentration of 5wt% or less of the 3rd refrigerant in all mixed non-azeotropic refrigerants of refrigerant circuit.
The refrigerating circulatory device of the present invention is preferably able to carry out the heating and cooling of heat load, and refrigerating circulatory device has：
Switching valve switches the direction of the refrigerant flowing in refrigerant circuit；Bridge circuit switches the refrigerant flowing in refrigerant circuit
Direction；And interflow path, so that the gas phase in the liquid phase and gas-liquid separator in gas-liquid separator is collaborated, the 3rd relief portion includes
Make the path that the liquid phase in gas-liquid separator is collaborated with the refrigerant flowed out from evaporator and constitutes.
Invention effect
According to the present invention, by carrying out gas-liquid separation to mixed non-azeotropic refrigerant, not to evaporator supply comprising a large amount of
The refrigerant of high boiling refrigerant (for example, R1234yf) but make its detour, thus, it is possible to relative to enclose in refrigerant return
The composition of the mix refrigerant on road greatly improves the low-boiling refrigerant in the mix refrigerant to circulate in refrigerant circuit
The mixed proportion of (for example, R32).Thereby, it is possible to temperature glide is fully suppressed to the degree that can fully avoid frosting.
According to the present invention, in enclosing the mix refrigerant in refrigerant circuit, the height of low GWP can be used as by increasing
The mixed proportion of the refrigerant of boiling point reduces GWP.
Description of the drawings
Fig. 1 is the figure for the structure for indicating the air conditioner (refrigerating circulatory device) involved by the 1st embodiment.
Fig. 2 is the p-h line charts of the refrigeration cycle involved by the 1st embodiment.
Fig. 3 is the figure for the structure for indicating the air conditioner involved by the variation of the 1st embodiment.
Fig. 4 is the figure (heating operation) for the structure for indicating the air conditioner involved by the 2nd embodiment.
Fig. 5 is the figure (refrigerating operaton) for the structure for indicating the air conditioner involved by the 2nd embodiment.
Fig. 6 is the figure (refrigerating operaton for the structure for indicating the air conditioner involved by the 2nd embodiment：Gas-liquid separation
When).
Fig. 7 is the temperature glide and (epimere), the figure of the temperature glide and (hypomere) of evaporation for indicating condensation.
Specific implementation mode
Hereinafter, refer to the attached drawing, embodiments of the present invention will be described.
(the 1st embodiment)
The air conditioner 1 of 1st embodiment shown in FIG. 1 is can to carry out room air (heat using outer gas as heat source
Load) heating i.e. heating refrigerating circulatory device.
Hereinafter, air conditioner 1 is illustrated, but structure described below equally can also be suitable for heating as heat
The refrigerating circulatory devices such as the water heater of the water of load.
Air conditioner 1, which has, includes compressor 3, the 1st heat exchanger 4, relief portion 5 (51~53) and the 2nd heat exchanger 6
Refrigerant circuit 2.Each important document for including in refrigerant circuit 2 is connected by being piped.
It is sealed with mixed non-azeotropic refrigerant in refrigerant circuit 2.
Compressor 3, relief portion 5 and the 2nd heat exchanger 6 constitute outdoor unit 7.2nd heat exchanger 6 is blown by fan 61
Outer gas and refrigerant between carry out heat exchange.
1st heat exchanger 4 constitutes indoor unit 8.1st heat exchanger 4 is in the room air and refrigeration blown by fan 41
Heat exchange is carried out between agent.
It is sealed with mixed non-azeotropic refrigerant in refrigerant circuit 2.Mixed non-azeotropic refrigerant is with indicated by an arrow in Fig. 1
Direction, recycled in refrigerant circuit 2.
The air conditioner 1 of present embodiment is not used in refrigeration and is only used for heating, therefore can omit switching refrigeration
The four-way valve 19 (switching valve) of the flow direction of agent.With switching refrigerant flow direction necessity independently, share outdoor
Machine unit, therefore refrigerant circuit 2 is constituted comprising four-way valve 19.
Air conditioner 1 carries out heating operation, therefore in present embodiment, and the 1st heat exchanger 4 is referred to as condenser 4, will
2nd heat exchanger 6 is referred to as evaporator 6.
The refrigerant of mixed non-azeotropic refrigerant mixing different boiling forms, the mixed non-azeotropic refrigerant of present embodiment
Including the R1234yf of the R32 as the 1st refrigerant, the 2nd refrigerant as boiling point ratio R32 high and as the 3rd refrigerant
CO2.R32 is HFC (hydrofluorocarbon (hydrofluorocarbon)) refrigerant, and R1234yf is HFO (Hydro Fluoro
Olefin (HF hydrocarbon)) refrigerant.
The mixed proportion i.e. concentration of the R32 in all mixed non-azeotropic refrigerants of refrigerant circuit 2 is enclosed with weight
% densimeters are measured, are 30~70wt%.
That is, by using condensing pressure, volume capacity and the excellent R32 of refrigeration effect, and fully improve GWP the small the 2nd
The mixed proportion of refrigerant (R1234yf) thus assures specified value GWP below.As enclosing in the mixing of refrigerant circuit 2
The mixed proportion of the composition of refrigerant, preferably the 2nd refrigerant is more than the mixed proportion of the 1st refrigerant.
Also, enclose the CO in all mixed non-azeotropic refrigerants of refrigerant circuit 22Mixed proportion, that is, concentration with
Weight % densimeters are 5wt% or less.The CO excellent by adding volume energy2, can realize the miniaturization of compressor 3.
As the 2nd refrigerant, additionally it is possible to replace R1234yf using R1234ze (E).At this point, by following explanation
" R1234yf " is replaced with " R1234ze (E) ".
Also, as the 2nd refrigerant, additionally it is possible to use R1234yf and R1234ze (E) both sides.
During air conditioner 1 carries out heating operation, the mixed non-azeotropic refrigerant flowed in evaporator 6 is (hereinafter, mixed
Close refrigerant) in R32 mixing ratio of the mixed proportion than enclosing the R32 in all mix refrigerants of refrigerant circuit 2
Example (for example, 40wt%) is high.Before the mixed proportion of R32 in the mix refrigerant flowed in evaporator 6 substantially 50wt%
(weight concentration) afterwards.
In order to realize that the mixed proportion when operations different from enclosed mixed proportion, air conditioner 1 have as described above
It is standby：Relief portion 51~53；Gas-liquid separator 11；1st path 121 supplies the system of the gas phase in gas-liquid separator 11 to evaporator 6
Cryogen；2nd path 122 does not supply evaporator 6 refrigerant of the liquid phase in gas-liquid separator 11 but makes its detour；In and
Between cooler 13 (heat exchanger between refrigerant).Also, by gas-liquid separator 11 to being flowed out from condenser 4 and being depressurized portion 51
The mix refrigerant of the gas-liquid two-phase of (the 1st relief portion) decompression carries out gas-liquid separation, makes to pass through centre from the gas phase of liquid phase separation
The backward evaporator 6 that cooler 13 carries out heat exchange to condense with liquid phase supplies, thus from the liquid refrigerant rich in R1234yf
The refrigerant rich in R32 of separation flows in evaporator 6.
That is, in the air conditioner 1 of present embodiment, by reducing all hybrid refrigerations enclosed in refrigerant circuit 2
The mixed proportion of R32 in agent simultaneously increases the mixed proportion of R1234yf while assuring specified value GWP below, to pass through packet
Circuit 10 containing gas-liquid separator 11 and intercooler 13, the mixing circulated in refrigerant circuit 2 when fully improving operation
The mixed proportion (apparent mixed proportion) of R32 in refrigerant.
As shown the relationship between temperature glide and the mixed proportion (concentration) of R32 in Fig. 7, more than as temperature glide
Peak 20wt% region, the mixed proportion (concentration) of R32 is higher, and temperature glide is smaller.
In present embodiment, by fully improving the apparent mixed proportion of R32, the temperature glide of evaporation inhibits to 7.0 DEG C
~7.5 DEG C or so.Thereby, it is possible to avoid generating the frosting to evaporator 6.Pass through condensing pressure, volume capacity and refrigeration effect
Mixed proportion ratio R1234yf high when the operation of excellent R32, the performance of air conditioner 1 are also improved, additionally it is possible to be helped
In miniaturization.
Hereinafter, with reference to figure 1 and Fig. 2, the circuit 10 comprising gas-liquid separator 11 and intercooler 13 is illustrated.Figure
In 1 and Fig. 2, corresponding position mark is identically numbered ((1), (2) etc.).
If also including the CO of dry measure in the mix refrigerant used in present embodiment2, but following theory is not interfered with substantially
The effect in bright circuit 10, therefore omit and be directed to CO2Record.CO2Boiling point ratio R32 and R1234yf it is low, therefore chatted following
In the operating process stated, the substantially state of gas phase.
The mix refrigerant used in present embodiment can not include CO2And it is only made of R32 and R1234yf.
Circuit 10 includes the relief portion 51~53 for constituting relief portion 5, gas-liquid separator 11, accumulator 110, intercooler
13 and constitute.
Relief portion 51~53, gas-liquid separator 11, accumulator 110 and intercooler 13 constitute outdoor unit 7.
Relief portion 51~53 makes mix refrigerant throttling expansion.These relief portions 51~53 are able to adjust throttling
Amount.
Relief portion 51 is between condenser 4 and gas-liquid separator 11.The relief portion 51 makes from the outlet (3) of condenser 4
The refrigerant of outflow is decompressed to the intermediate pressure p1 (with reference to figure 2) (4) of the state as gas-liquid two-phase.According to the section of relief portion 51
Flow, the pressure (intermediate pressure p1) of control supply to the refrigerant of gas-liquid separator 11.According to intermediate pressure p1, gas is determined
Aridity in liquid/gas separator 11.
The refrigerant of gas-liquid two-phase Jing Guo relief portion 51 is separated into gas phase and liquid phase by gas-liquid separator 11.
The mix refrigerant of the intermediate pressure p1 of gas-liquid two-phase is decompressed to by relief portion 51 with high boiling R1234yf ratios
The more liquefied states of R32 flow into gas-liquid separator 11.
The refrigerant flowed into is in gas-liquid separator 11, according to aridity corresponding with intermediate pressure p1 by gas-liquid point
From.It stores in the saturated solution (5) of gas-liquid separator 11, includes more R1234yf than R32.Liquid in gas-liquid separator 11
Mutually supplied to the low temperature path 13L of intercooler 13 via accumulator 110.
In gas-liquid separator 11, the refrigerant of liquid phase bypasses evaporator 6 by the 2nd path 122 (detour path).Fig. 1 and
In Fig. 2, it is represented by dotted lines the 2nd path 122.
Accumulator 110 receives liquid refrigerant from gas-liquid separator 11 and stores.It is more than defined liquid in accumulator 110
The liquid refrigerant of position is flowed into the low temperature path 13L of intercooler 13.In order to store the liquid refrigerating for being rich in R1234yf
Agent increases the mixed proportion of the R32 in the mix refrigerant flowed in evaporator 6, preferably has by liquid in the 2nd path 122
Device 110.
Gas-liquid separation situation in gas-liquid separator 11 is determined according to aridity corresponding with intermediate pressure p1.This embodiment party
In formula, not to liquid refrigerant of the supply of evaporator 6 rich in R1234yf but makes its detour, only make the richness with the liquid phase separation
Refrigerant containing R32 flows into evaporator 6, thus makes the mixed proportion ratio of the R32 in the mix refrigerant flowed in evaporator 6
Actual mixed proportion (mixed proportion for enclosing the R32 in all mix refrigerants of refrigerant circuit 2) is high.
Wherein, since the mixed proportion for enclosing the R1234yf in all mix refrigerants of refrigerant circuit 2 is high, because
This can greatly improve inflow evaporator by detaching the mainly liquid refrigerant comprising R1234yf and it being made to bypass evaporator 6
The mixed proportion of R32 in 6 mix refrigerant, and correspondingly reduce temperature glide.
In present embodiment, the intermediate pressure of the aridity of gas-liquid separator 11 is determined by 51 suitable control of relief portion
P1 can improve the apparent mixed proportion of R32 to keep temperature glide fully small.
As gas-liquid separator 11, the gas-liquid separator of well known mode appropriate can be used.For example, can use：
By the way that refrigerant is set as static condition in storage tank, the gravity point of gas phase and liquid phase is detached according to the difference (density contrast) of proportion
From formula；The flowing of convolution is assigned to refrigerant to centrifuge the mode of gas phase and liquid phase；And it is being set to flow path inner peripheral portion
Serpentine canal keeps the surface tension formula etc. of liquid.
From the viewpoint of so that outdoor unit 7 is minimized, formula and surface tension formula are preferably centrifuged.
Pass through the high temperature path 13H of intercooler 13, supply by the gas phase (6) of gas-liquid separator 11 and liquid phase separation
To evaporator 6.
Intercooler 13 has the low temperature path 13L that flowing has the high temperature path 13H of gas phase and flowing to have liquid phase.High temperature
Path 13H is equivalent to the part in the 1st path 121 that the gas phase in gas-liquid separator 11 is supplied to evaporator 6.Low temperature path
13L is equivalent to the part for not supplying the liquid phase in gas-liquid separator 11 to evaporator 6 but making its 2nd path 122 detoured.
Intercooler 13 make the gas phase flowed in the 13H of high temperature path and the liquid phase that is flowed in the 13L of low temperature path it
Between carry out heat exchange.By heat exchange, the gas phase of high temperature path 13H radiates to the liquid phase of low temperature path 13L and is condensed.It is cold
Solidifying refrigerant flows into evaporator 6, after the heat exchange gasification with outer gas, can make to obtain energy variation by latent heat
Refrigeration cycle set up.
It is preferred that the gas phase flowed out from gas-liquid separator 11 is condensed by intercooler 13 to saturated solution (7).
Relief portion 52 (the 2nd relief portion) is located at the high temperature path 13H of intercooler 13 and than it in the 1st path 121
Between evaporator 6 farther downstream.The refrigerant flowed out from high temperature path 13H is decompressed to work according to the amount of restriction of relief portion 52
For the evaporating pressure p2 (8) for the pressure that evaporation starts, evaporator 6 is flowed into.As above-mentioned, what is flowed into is the mixing system rich in R32
Cryogen.The mix refrigerant flowed in evaporator 6 is evaporated (9) by absorbing heat from outer gas.
On the other hand, the liquid phase of the low temperature path 13L of outflow intercooler 13 passes through the decompression positioned at the 2nd path 122
After (10) are depressurized in portion 53 (the 3rd relief portion), amount evaporation corresponding with the amount absorbed heat from the gas phase of high temperature path 13H.2nd path
122 are connected to the path (11) for the low pressure refrigerant that flowing has from the outlet outflow of evaporator 6.By the shadow of the low pressure refrigerant
It rings, in side farther downstream than relief portion 53, refrigerant is downstreamed while evaporating to be flowed.
In Fig. 2, as an example, the p-h line charts of air conditioner 1 are schematically illustrated.With reference to figure 2, to refrigerant circuit 2
Effect illustrate.
The refrigerant (1) of the high temperature and pressure to spue from compressor 3 flows into (2) to condenser 4.By condenser 4 to interior
The refrigerant (3) that air radiates and condenses is decompressed to intermediate pressure p1 by relief portion 51, to the state as gas-liquid two-phase
(4), by gas-liquid separator 11 by gas-liquid separation (5) (6).
Pass through intercooler 13 and liquid phase by the gas phase (6) rich in R32 that gas-liquid separator 11 is detached with liquid phase (5)
(5) heat exchange is carried out, is thus condensed (7).Moreover, being decompressed to (8) after evaporating pressure p2 by relief portion 52, evaporation is flowed into
Device 6.The mixed proportion of R32 in the mix refrigerant flowed in evaporator 6 is high, therefore evaporates start temperature and terminate with evaporation
The temperature glide of temperature is small.The gas refrigerant (9) evaporated by evaporator 6 is supplied to compressor 3.
On the other hand, liquid phase (5) depressurizes (10), moreover, in after by accumulator 110 by relief portion 53
Between cooler 13 towards the terminal (11) in the 2nd path 122, downstream while evaporating and flow.
According to the present embodiment, gas-liquid separation is the liquid refrigerant rich in R1234yf and the gas refrigeration rich in R32
Agent not to refrigerant of the supply of evaporator 6 rich in R1234yf but makes its detour, and thus, it is possible to improve the mixed proportion of R32
It is set to be flowed into evaporator 6 to the degree reversed from the composition enclosed in the mix refrigerant of refrigerant circuit 2.It is warm as a result,
Degree sliding is inhibited, therefore can avoid the frosting to evaporator 6.
Also, the composition for flowing into the mix refrigerant of condenser 4 by compressor 3 from evaporator 6 is also enriched in R32, therefore
It can also inhibit the temperature glide of condensation.
By the above, the range of operation of air conditioner 1 can be made to be set up throughout wider range of operation.
Air conditioner 1 according to the present embodiment, is enclosed in the mixed non-azeotropic refrigerant of refrigerant circuit 2, is made
Mixed proportion for the R1234yf of low GWP is high, therefore can realize the GWP less than 300.
The case where gas-liquid separation the aridity depending on gas-liquid separator corresponding with intermediate pressure p1 11, therefore pass through root
Intermediate pressure p1 is controlled according to the amount of restriction of relief portion 51, gas-liquid separation situation can be controlled.Intermediate pressure p1 is for example preferably controlled
Become in the range of 0.3~0.5 at aridity.In order to make refrigeration cycle normally set up, such as can be true by the lower limit of aridity
It is set to 0.1.
It is preferred that considering the revenue and expenditure of energy, it is set by the flow of the liquid phase (5) and gas phase (6) of 11 branch of gas-liquid separator.
For example, when the aridity of gas-liquid separator 11 is 0.5, so that the mode of liquid phase (1: 1) equal with the flow of gas phase, adjustment the 2nd
52 respective amount of restriction of relief portion 51 and the 3rd relief portion.
(variation of the 1st embodiment)
In air conditioner 1 shown in Fig. 3, have in the 2nd path 122：Accumulator 110；And valve 14, it is opened and closed gas-liquid separation
Flow path 11A between device 11 and accumulator 110.
If illustrated in the 1st embodiment, if the gas phase of gas-liquid separator 11 is made to flow into evaporator 6, and make gas-liquid point
Liquid phase from device 11 is run while detour, then the liquid level in accumulator 110 increases.
The accumulator 110 and valve 14 for being respectively positioned on the 2nd path 122 can be utilized, such control as described below is carried out.
The opportunity appropriate of liquid refrigerant is stored in accumulator 110, closes valve 14, is stopped from gas-liquid separator 11
To the Liquid acquisition of accumulator 110.At this point, open relief portion 53 (aperture is standard-sized sheet).
If continuing to run in this state, to be pulled to the low pressure in the path for the terminal (11) for being connected with the 2nd path 122
Mode, the liquid refrigerant in accumulator 110 downstreams while evaporating and flows towards terminal (11).At this point, main
It is low-boiling R32 evaporations, is released from the terminal (11) in the 2nd path 122.The refrigerant rich in R32 being released is to compressor 3
Sucking, and recycled in refrigerant circuit 2, thus the mixed proportion when operation of R32 is improved.
With the releasing of the refrigerant rich in R32, in the 2nd path 122, R1234yf is concentrated.
Control as stated above can be rich in from by gas-liquid separator 11 with what the gas phase rich in R32 detached
The liquid refrigerant of R1234yf, further extract the refrigerant rich in R32 come to refrigerant circuit 2 release, therefore can more into
One step increases the mixed proportion when operation of R32.
R32 described above is released control and can be repeated with defined frequency.If the operational mode knot that R32 is released
Beam can then open valve 14, and set the amount of restriction of relief portion 53, be transitioned into identical with the explanation in the 1st embodiment
Usual operational mode.
In addition, can be as follows, that is, the liquid level in detection accumulator 110 is opened if starting liquid level or more as defined in being stored as
Beginning R32 releases operational mode, if the liquid level in accumulator 110 is less than defined end liquid level, terminates R32 and releases operation mould
Formula.
It also allows for replacing valve 14, use can be changed flows in the flow path 11A between gas-liquid separator 11 and accumulator 110
The flow rate regulating valve of the flow of dynamic refrigerant carries out identical control.
That is, replacing opening valve 14, increase the flow of flow path 11A by flow rate regulating valve, instead of closing valve 14, passes through flow
Adjust the flow that valve reduces flow path 11A.
(the 2nd embodiment)
Then, with reference to fig. 4 to fig. 6, the 2nd embodiment is illustrated.
Air conditioner 9 involved by 2nd embodiment can carry out room air (heat load) using outer gas as heat source
Heating and cooling.That is, air conditioner 9 is used for refrigeration purposes and the purposes that heats.
Fig. 4 to fig. 6 indicates the structure that identical air conditioner 9 has.
In air conditioner 9, switch the flow direction of refrigerant by four-way valve 19, it is shown in Fig. 4 thus, it is possible to carry out
Heating operation and Fig. 5 and refrigerating operaton shown in fig. 6.
When heating operation (Fig. 4), the 1st heat exchanger 4 is functioned as condenser, and the 2nd heat exchanger 6 is used as evaporator
It functions.
When refrigerating operaton (Fig. 5 and Fig. 6), the 1st heat exchanger 4 is functioned as evaporator, 6 conduct of the 2nd heat exchanger
Condenser functions.
In fig. 4 to fig. 6, the discharge opening of compressor 3 is indicated to the path of the entrance of evaporator, with double dot dash line table with solid line
Show the path of the suction inlet for being exported to compressor 3 of evaporator.
Hereinafter, being with the air conditioner 9 of the 2nd embodiment item different from the air conditioner 1 of the 1st embodiment
Center illustrates.
As shown in figure 4, in air conditioner 9, instead of the relief portion 53 of the 1st embodiment of throttling expansion, have：It detours
Section 15A (is represented by dotted lines), is directed through the liquid phase that gas-liquid separator 11 is detached with gas phase；And open and close valve 151, opening and closing are detoured
Section 15A.
The terminal of detour section 15A, which is connected to, to flow out from evaporator 6 and towards the path 15B of compressor 3.Detour section
15A is equivalent to the 3rd relief portion of the pressure for reducing refrigerant.
By detour section 15A and path 15B, constitute liquid phase in gas-liquid separator 11 is not supplied to evaporator 6 but
The 2nd path 122 for making it detour.
Also, air conditioner 9 is not only in heating operation, in refrigerating operaton, also according to needs, into being about to from condensation
The refrigerant of device (4,6) outflow carries out gas-liquid separation after being decompressed to the state of gas-liquid two-phase, and the refrigerant rich in R32 is made to flow into
The processing of evaporator (6,4).
Air conditioner 9 has bridge circuit 16, so that the processing is set up in heating operation and when refrigerating operaton.
Bridge circuit 16 is made of 4 check-valves 161~164 that the flow direction of refrigerant is determined as to a direction.
(heating operation)
With reference to figure 4, heating operation is illustrated.
When heating operation, open and close valve 151 is opened, opens detour section 15A in advance.
Also, in advance close in order in refrigerating operaton without gas-liquid separation the case where and prepare in accumulator 110
Interflow path 17 open and close valve 171.Collaborate path 17 and links the interior gas phase in extraction gas-liquid separator 11 of accumulator 110
1st path 121.
In addition, in fig. 4 to fig. 6, the valve closed is indicated with black.
The refrigerant flowed out from condenser 4 is decompressed to the intermediate pressure of gas-liquid two-phase by relief portion 51, passes through bridge circuit
16 check-valves 161 is flowed into gas-liquid separator 11.Liquid phase in gas-liquid separator 11 is via accumulator 110 to detour section
15A is flowed into, and is subtracted by the influence of the low pressure refrigerant flowed in the path 15B for being connected to the terminal of detour section 15A
Pressure is collaborated with the refrigerant flowed in the 15B of path.Also, towards while evaporating the flowing of compressor 3 in the 15B of path.
Path 15B includes the low temperature path 13L of intercooler 13.
It is flowed in the high temperature path 13H of intercooler 13 with the gas phase of liquid phase separation in gas-liquid separator 11, with
The refrigerant flowed in the 13L of low temperature path carries out heat exchange, thus condenses.Also, by the check-valves of bridge circuit 16 163,
It is flowed by the backward evaporator 6 of 52 decompression of relief portion.
(refrigerating operaton)
Then, with reference to figure 5 and Fig. 6, refrigerating operaton is illustrated.
When about refrigerating operaton, on the contrary, being therefore referred to as the 1st heat exchanger 4 when the direction of refrigeration cycle and heating operation
2nd heat exchanger 6 is referred to as condenser 6 by evaporator 4.
It is exchanged when as it does so, relief portion 51 and 52 respective function of relief portion are with heating operation.
When refrigerating operaton, relief portion 52, which is equivalent to, makes the pressure of the refrigerant flowed out from condenser 6 reduce to gas-liquid two-phase
State the 1st relief portion, relief portion 51 is equivalent to the refrigerant for making to be flowed in the 1st path 121 with liquid phase gas-liquid separation
Pressure reduce the entrance to evaporator 4 pressure the 2nd relief portion.
When refrigerating operaton, the temperature difference between the refrigerant flowed in evaporator 4 and heat load (room air) is small, because
This only in the case where being possible to generate frosting due to the relationship with temperature glide, carries out the apparent mixed proportion for improving R32
Processing inhibit temperature glide.
Here, when the temperature of the room air detected by sensor 18 is less than specified value, inhibition temperature glide is carried out
Processing (Fig. 6), when the temperature of room air is specified value or more, without the processing (Fig. 5).It is being evaporated in addition, also detecting
The temperature of the refrigerant flowed in device 4, additionally it is possible to according to the detection temperature difference of the temperature and room air, determine whether to carry out
Inhibit the processing of temperature glide.Furthermore it is possible to use determinating reference appropriate.
First, fully big to the temperature difference of the refrigerant and room air that are flowed in evaporator 4 with reference to figure 5, therefore not
It carries out inhibiting the phenomenon that the processing of temperature glide illustrates.
At this point, closing the open and close valve 151 of detour section 15A, the opening and closing in the interflow path 17 prepared in accumulator 110 is opened
Valve 171.
Liquid phase in gas-liquid separator 11 is flowed into via accumulator 110 to interflow path 17, from interflow path 17 to the 1st tunnel
Diameter 121 flows out.That is, the refrigerant flowed out from gas-liquid separator 11 with liquid phase state with from gas-liquid separator 11 with gas phase state stream
The refrigerant interflow gone out.
If in addition, ensuring there is sufficient capacity in gas-liquid separator 11, accumulator 110 is simultaneously nonessential.
It exports and flows out from condenser 6, and the refrigeration of intermediate pressure is decompressed to by the 1st relief portion (being herein relief portion 52)
Agent is flowed by the check-valves 164 of bridge circuit 16 to gas-liquid separator 11.In the gas-liquid separator 11, refrigerant detaches for the time being
For liquid phase and gas phase, but these liquid phases collaborate (with reference to the 20 of figure 5) with gas phase later.That is, without making in gas-liquid separator 11
Liquid phase rich in R1234yf detour, therefore supplied with one evaporator 4 in the same direction of gas phase.During the refrigerant collaborated passes through on one side
Between cooler 13 high temperature path 13H, on one side in the 13L of low temperature path refrigerant carry out heat exchange, pass through bridge circuit 16
Check-valves 162 after further being depressurized by the 2nd relief portion (being herein relief portion 51), is flowed into evaporator 4.
Then, with reference to figure 6, to carrying out inhibiting the phenomenon that the processing of temperature glide illustrates.
At this point, it is identical as (Fig. 4) when heating operation, the open and close valve 151 of detour section 15A is opened, is closed in accumulator 110
The open and close valve 171 in the interflow path 17 of preparation, is thus separated into gas phase and liquid phase by the refrigerant for being decompressed to intermediate pressure.
If in addition, also carrying out inhibiting the processing of temperature glide always in refrigerating operaton, it is not necessarily to open and close valve 151.
The liquid phase flowed into from gas-liquid separator 11 to detour section 15A via accumulator 110 in the 15B of path by flowing
Low pressure refrigerant influence and be depressurized, towards while evaporating the flowing of compressor 3 in the 15B of path.
With the gas phase rich in R32 of liquid phase separation by being flowed with from path 15B to low temperature path 13L in gas-liquid separator 11
The refrigerant entered carries out heat exchange, is thus condensed.Also, after being depressurized by the 2nd relief portion (relief portion 51), pass through bridge electricity
The check-valves 162 on road 16 is flowed into evaporator 4.
By the above, the apparent mixed proportion of the R32 recycled in refrigerant circuit 2 can be improved, therefore even if inhibiting
In the case that the temperature difference of temperature glide, room air and refrigerant temperature is big, the frosting to evaporator 4 can be also avoided.
In the same manner as the variation (Fig. 3) of the 1st embodiment, (Fig. 4) and refrigeration in the heating operation of the 2nd embodiment
When operation (Fig. 6), it can carry out utilizing accumulator 110 and valve 14, release and be rich in from the 2nd path 122 to refrigerant circuit 2
The control of the refrigerant of R32.
In addition to the foregoing, without departing from spirit of the invention, then it can accept or reject and be enumerated in selection the above embodiment
Structure, or suitably change as other structures.
As the mixed non-azeotropic refrigerant in the present invention, the refrigerant appropriate of different boiling can be used.Enclose in
In the mix refrigerant of refrigerant circuit, by increasing the mixed proportion for the high boiling refrigerant for being used as low GWP, it can reduce
GWP。
Symbol description
1- air conditioners (refrigerating circulatory device), 2- refrigerant circuits, 3- compressors, the 1st heat exchangers of 4-, 5- decompressions
Portion, 51~53- relief portions, the 2nd heat exchangers of 6-, 7- outdoor units, 8- indoor units, 9- air conditioners (refrigerating circulatory device),
The circuits 10-, 11- gas-liquid separators, 11A- flow paths, 110- accumulators, the 1st paths 121-, the 2nd paths 122-, 13- cooling during rollings
Device, 13H- high temperature path, 13L- low temperature path, 14- valves, 15A- detours section (the 3rd relief portion, path), the paths 15B-, 151-
Open and close valve, 16- bridge circuits, 161~164- check-valves, the interflow 17- path, 171- open and close valves, 18- sensors, 19- four-way valves,
P1- intermediate pressures, p2- evaporating pressures.
Claims (according to the 19th article of modification of treaty)
1. a kind of (after correction) refrigerating circulatory device, is sealed with mixed non-azeotropic refrigerant, have comprising compressor, the 1st heat
Exchanger, relief portion and the 2nd heat exchanger and the refrigerant circuit constituted, and the heating of heat load can be carried out, the refrigeration
Circulator is characterized in that having：
1st relief portion makes from the condenser outflow as any of the 1st heat exchanger and the 2nd heat exchanger
The pressure of the mixed non-azeotropic refrigerant reduce to the state of gas-liquid two-phase；
The mixed non-azeotropic refrigerant for the state for being decompressed to the gas-liquid two-phase is separated into gas phase and liquid by gas-liquid separator
Phase；
1st path, to as described in another the evaporator supply in the 1st heat exchanger and the 2nd heat exchanger
The refrigerant of gas phase in gas-liquid separator；
2nd path does not supply the evaporator refrigerant of the liquid phase in the gas-liquid separator but makes its detour；
Intercooler passes through the refrigerant for making the refrigerant flowed in the 1st path with being flowed in the 2nd path
Between carry out heat exchange and make its condensation；
2nd relief portion makes the pressure of the refrigerant flowed in the 1st path reduce；And
3rd relief portion makes the pressure of the refrigerant flowed in the 2nd path reduce,
2nd path has：
Accumulator receives liquid phase from the gas-liquid separator；And
The system that valve, the flow path that can be opened and closed between the gas-liquid separator and the accumulator or adjustment are flowed in the flow path
The flow of cryogen.
(2. deletion)
(3. after correction) refrigerating circulatory device according to claim 1, which is characterized in that
The mixed non-azeotropic refrigerant include the R32 as the 1st refrigerant and R1234yf as the 2nd refrigerant and
At least one of R1234ze (E),
Enclose a concentration of 30 of the 1st refrigerant in all mixed non-azeotropic refrigerants of the refrigerant circuit
~70wt%..
4. refrigerating circulatory device according to claim 3, which is characterized in that
The mixed non-azeotropic refrigerant includes the CO as the 3rd refrigerant2,
Enclose a concentration of of the 3rd refrigerant in all mixed non-azeotropic refrigerants of the refrigerant circuit
5wt% or less.
The refrigerating circulatory device of (5. after correction) according to claim 1,3, any one of 4, which is characterized in that
The heating and cooling of the heat load can be carried out,
The refrigerating circulatory device has：
Switching valve switches the direction of the refrigerant flowing in the refrigerant circuit；
Bridge circuit switches the direction of the refrigerant flowing in the refrigerant circuit；And
Collaborate path, the liquid phase in the gas-liquid separator made to collaborate with the gas phase in the gas-liquid separator,
3rd relief portion includes to make the path of liquid phase and the refrigerant interflow flowed out from the evaporator in the gas-liquid separator
And it constitutes.
Claims (5)
1. a kind of refrigerating circulatory device, is sealed with mixed non-azeotropic refrigerant, has comprising compressor, the 1st heat exchanger, subtracts
Splenium and the 2nd heat exchanger and the refrigerant circuit constituted, and the heating of heat load can be carried out, the refrigerating circulatory device
It is characterized in that having：
1st relief portion makes from the condenser outflow as any of the 1st heat exchanger and the 2nd heat exchanger
The pressure of the mixed non-azeotropic refrigerant reduce to the state of gas-liquid two-phase；
The mixed non-azeotropic refrigerant for the state for being decompressed to the gas-liquid two-phase is separated into gas phase and liquid by gas-liquid separator
Phase；
1st path, to as described in another the evaporator supply in the 1st heat exchanger and the 2nd heat exchanger
The refrigerant of gas phase in gas-liquid separator；
2nd path does not supply the evaporator refrigerant of the liquid phase in the gas-liquid separator but makes its detour；
Intercooler passes through the refrigerant for making the refrigerant flowed in the 1st path with being flowed in the 2nd path
Between carry out heat exchange and make its condensation；
2nd relief portion makes the pressure of the refrigerant flowed in the 1st path reduce；And
3rd relief portion makes the pressure of the refrigerant flowed in the 2nd path reduce.
2. refrigerating circulatory device according to claim 1, which is characterized in that
Have in the 2nd path：
Accumulator receives liquid phase from the gas-liquid separator；And
The system that valve, the flow path that can be opened and closed between the gas-liquid separator and the accumulator or adjustment are flowed in the flow path
The flow of cryogen.
3. refrigerating circulatory device according to claim 1 or 2, which is characterized in that
The mixed non-azeotropic refrigerant include the R32 as the 1st refrigerant and R1234yf as the 2nd refrigerant and
At least one of R1234ze (E),
Enclose a concentration of 30 of the 1st refrigerant in all mixed non-azeotropic refrigerants of the refrigerant circuit
~70wt%.
4. refrigerating circulatory device according to claim 3, which is characterized in that
The mixed non-azeotropic refrigerant includes the CO as the 3rd refrigerant2,
Enclose a concentration of of the 3rd refrigerant in all mixed non-azeotropic refrigerants of the refrigerant circuit
5wt% or less.
5. refrigerating circulatory device according to any one of claim 1 to 4, which is characterized in that
The heating and cooling of the heat load can be carried out,
The refrigerating circulatory device has：
Switching valve switches the direction of the refrigerant flowing in the refrigerant circuit；
Bridge circuit switches the direction of the refrigerant flowing in the refrigerant circuit；And
Collaborate path, the liquid phase in the gas-liquid separator made to collaborate with the gas phase in the gas-liquid separator,
3rd relief portion includes to make the path of liquid phase and the refrigerant interflow flowed out from the evaporator in the gas-liquid separator
And it constitutes.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-061136 | 2016-03-25 | ||
| JP2016061136A JP6774769B2 (en) | 2016-03-25 | 2016-03-25 | Refrigeration cycle equipment |
| PCT/JP2017/011839 WO2017164333A1 (en) | 2016-03-25 | 2017-03-23 | Refrigerating cycle apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108463676A true CN108463676A (en) | 2018-08-28 |
| CN108463676B CN108463676B (en) | 2020-06-23 |
Family
ID=59900627
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780006360.4A Active CN108463676B (en) | 2016-03-25 | 2017-03-23 | Refrigeration cycle device |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3396273A4 (en) |
| JP (1) | JP6774769B2 (en) |
| CN (1) | CN108463676B (en) |
| AU (1) | AU2017238687B2 (en) |
| WO (1) | WO2017164333A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112955520A (en) * | 2018-10-26 | 2021-06-11 | 科慕埃弗西有限公司 | Compositions comprising difluoromethane, tetrafluoropropene, and carbon dioxide and uses thereof |
| CN113108503A (en) * | 2021-03-24 | 2021-07-13 | 中国科学院工程热物理研究所 | Heat pump set based on self-cascade circulation |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI794296B (en) * | 2017-10-12 | 2023-03-01 | 美商科慕Ｆｃ有限責任公司 | Compositions containing difluoromethane, tetrafluoropropene, and carbon dioxide and uses thereof |
| TW202317734A (en) * | 2017-10-12 | 2023-05-01 | 美商科慕Ｆｃ有限責任公司 | Compositions containing difluoromethane, tetrafluoropropene, and carbon dioxide and uses thereof |
| JP2023136032A (en) * | 2022-03-16 | 2023-09-29 | 株式会社富士通ゼネラル | Refrigeration cycle device |
| CN115036543B (en) * | 2022-06-20 | 2023-11-07 | 潍柴动力股份有限公司 | Hydrogen fuel cell, control method and control device thereof |
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| JPS6458964A (en) * | 1987-08-29 | 1989-03-06 | Daikin Ind Ltd | Heat pump system |
| CN101665681A (en) * | 2008-07-30 | 2010-03-10 | 霍尼韦尔国际公司 | compositions containing difluoromethane and fluorine substituted olefins |
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| CN102523753A (en) * | 2010-09-08 | 2012-06-27 | 松下电器产业株式会社 | Refrigeration cycle apparatus |
| WO2015140879A1 (en) * | 2014-03-17 | 2015-09-24 | 三菱電機株式会社 | Refrigeration cycle device |
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| JP2012236884A (en) * | 2011-05-10 | 2012-12-06 | Fujitsu General Ltd | Mixed refrigerant and air conditioner using the same |
| CN106104170B (en) * | 2014-03-17 | 2019-10-25 | 三菱电机株式会社 | Refrigerating circulatory device |
-
2016
- 2016-03-25 JP JP2016061136A patent/JP6774769B2/en active Active
-
2017
- 2017-03-23 EP EP17770373.3A patent/EP3396273A4/en not_active Withdrawn
- 2017-03-23 WO PCT/JP2017/011839 patent/WO2017164333A1/en active Application Filing
- 2017-03-23 AU AU2017238687A patent/AU2017238687B2/en active Active
- 2017-03-23 CN CN201780006360.4A patent/CN108463676B/en active Active
Patent Citations (5)
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| JPS6458964A (en) * | 1987-08-29 | 1989-03-06 | Daikin Ind Ltd | Heat pump system |
| CN102066852A (en) * | 2008-06-16 | 2011-05-18 | 三菱电机株式会社 | Non-azeotropic refrigerant mixture and refrigeration cycle device |
| CN101665681A (en) * | 2008-07-30 | 2010-03-10 | 霍尼韦尔国际公司 | compositions containing difluoromethane and fluorine substituted olefins |
| CN102523753A (en) * | 2010-09-08 | 2012-06-27 | 松下电器产业株式会社 | Refrigeration cycle apparatus |
| WO2015140879A1 (en) * | 2014-03-17 | 2015-09-24 | 三菱電機株式会社 | Refrigeration cycle device |
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| CN112955520A (en) * | 2018-10-26 | 2021-06-11 | 科慕埃弗西有限公司 | Compositions comprising difluoromethane, tetrafluoropropene, and carbon dioxide and uses thereof |
| CN113108503A (en) * | 2021-03-24 | 2021-07-13 | 中国科学院工程热物理研究所 | Heat pump set based on self-cascade circulation |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2017164333A1 (en) | 2017-09-28 |
| CN108463676B (en) | 2020-06-23 |
| AU2017238687B2 (en) | 2019-07-18 |
| AU2017238687A1 (en) | 2018-07-19 |
| JP2017172908A (en) | 2017-09-28 |
| EP3396273A4 (en) | 2019-01-23 |
| JP6774769B2 (en) | 2020-10-28 |
| EP3396273A1 (en) | 2018-10-31 |
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